Cross rolling machine



1934- L. BECKER CROSS ROLLING MACHINE 5 Sheets-Sheet 1 Filed March 7, 1936 INVENTOR Aug. 14, 1934; BECKER 1,970,121

CROSS ROLLING MACHINE Filed March 7. 1930 5 Sheet-Sheet 2 INVENTOR CROSS ROLLING MACHINE 5 Sheets-Sheet 3 Filed March 7. 1930 INVENTOR Aug. 14, 1934. L, BECKER- 1,970,121

CROSS ROLLING MACHINE Filed March '7, 1930 5 Sheets-Sheet 4 1ll/ llllfi INVEN TOR Lu M,

Qgum PM M Filed March 7. 1930 5 Sheets-Sheet 5 INVENTOR Patented Aug. 14, 1934 UNITED STATES PATENT OFFICE Application March '7, 1930, Serial No. 434,102 In Germany March 11, 1929 Claims.

This invention relates to cross rolling machines and provides numerous features of construction and operation which permit of wide variations in the operation, permit the construction of a machine at low cost, whereby the desired adjustments may be effected, and the machine is economical in operation.

In cross rolling a tube the setting of the rolls is very important and alterations in the setting have marked effect. Starting with a billet of a given diameter, the same may be enlarged to a tube of given nominal diameter, but by changing the angular setting of the cross rolls and correspondingly changing the plug or mandrel, the thickness and elongation, the rate of self-feeding, etc., may be varied as desired.

Considering the case of conical rolls, it will be seen that the vertex of the cone of which the active roll surface is a part may lie in the axis of the billet or tube being rolled, or may lie to the same side of said axis as does the roll body, or may lie on that side of said axis opposite that on which said roll body lies. In the first instance, there is no twisting of the metal during rolling, the action being comparable to two cones rolling on one another and having a common apex. Neither is there any tendency to feed the metal forward, and such feeding must be done by a separate force, as, for example, by a pusher or by auxiliary rolls.

In the second type of roll-setting above mentioned, there is a forward twisting of the metal causing elongation of the billet and a smaller wall thickness for the same medium tube diameter. It will, of course, be necessary to use a different mandrel than in the first case referred to. In the third case referred to, the final cross section of the metal as it leaves the rolls will be thicker than in the case first given, again requiring a different mandrel; but there is also a shortening of the billet and a backward twisting. It will be seen therefore, that by adjusting the rolls in the manner above described, I am able to vary at will the forward or backward twist and to produce, from the same solid or hollow billet a variety of tubes of the same medium tube diameter but of varying wall thickness. Furthermore, by suitable adjusting of the rolls, a wide variety in tube sizes can be had. Therefore it is possible with a single machine to produce a range of products not heretofore obtainable except at the expense of a large number of mills.

While the billet may be fed in any suitable T manner, it is desirable, as explained in my copending application, Serial No. 413,051, filed December 1D, 1929, to employ a pusher for feeding the billet through the mill.

Where the tube is enlarged, it has been common practice to so engage the billet by the cross rolls as to preliminarily throttle or reduce it in area and thus insure proper gripping and forward feeding. This results in large power losses which may be overcome by employing a pusher. It is desirable, however, that the pusher be of such form as to continue to engage the billet and push it forwardly over all or a large part of the working zone.

It is further desirable that the rolls be so mounted and arranged that their obliquity to the axis of the material may be adjusted in planes at an angle to one another and provision should also be made for adjusting the distance of the working surface of the rolls from the axis of the material. This last adjustment is preferably made by moving the rolls along their own axes. It is also desirable that a singleadjustment shall effect adjusting movement of each of the several cross rolls employed. By combining a pusher mechanism with a mill of this character it is possible to roll the material under conditions best suited to obtain the desired product with a minimum of power.

However, it is also necessary that rolls of different shapes shall be available, in order that the widest range of operation may be had. Therefore, I provide cross rolls made up of a plurality of parts, one or more of which parts may be replaced by parts of other size or shape for handling difierent sized tubes or billets. In this manner material economies may be effected, since the number of roll sections which must be carried in stock is relatively low, the parts are small as compared with full rolls, and therefore easily handled and stored. By combining different sections, a wide variety of roll contours may be obtained, and, coupled with the universal adjustment provided by my machine, it is possible to secure the best rolling conditions for any product.

In the accompanying drawings, illustrating present preferred embodiments of the invention,

Figure 1 is a top plan View, partly diagram matic, of a cross rolling machine showing one manner of adjusting the rolls;

Figure 2 is a sectional view taken on the line IIII of Figure l, but with the spindles adjusted to a position in said line for clearness in illustration;

Figure 3 is a diagrammatic View illustrating the driving of the pusher;

Figure 4 is a vertical section through another form of mill, illustrating mechanism for adjusting the rolls;

Figure 5 is a view to enlarged scale showing only one of the cross rolls, the mandrel and the pusher;

Figure 6 is a diagrammatic view illustrating the relationship between the rolls, the mandrel and the pusher;

Figure '7 is a view showing a modification;

Figures 8 and 9 are views showing sectional rolls;

Figures 10, 11 and 12 are diagrammatic views illustrating my improved method;

Figure 13 is a diagrammatic view illustrating a concave roll which may be employed; and

Figures 14, 15 and 16 are diagrammatic views illustrating ring-like rolls which may be employed.

The mill shown in Figures 1 to 3 inclusive comprises a base 2 having bed plates 3 carried thereby, the bed plates being pivotally mounted on a pin 4. The base 2 is provided with a fixed gear 5, and pinions 6 meshing therewith are carried by the bed plates 3. These pinions mesh with gears '7 keyed to shafts 8 which are journaled in the bed plates 3. The shafts 8 are secured at theirupper ends to frame members 9 slidable on top of the bed plates 3. It will be seen that as the bed plates 3 are moved around th central pin 4, the gearing causes the frame members 9 to swing and to assume fixed predetermined positions. The frame members 9 carry cross rolls 10 mounted in shafts 11, and the position of the cross rolls is determined by the movement of the bed plates 3. Various adjusted positions are indicated in Figure 1, and it will be noted that while in the illustration given the cross rolls in each position are effective for handling a billet of a given diameter, and enlarging the same to a tube of given diameter, the conditions of rolling are widely varied.

The mechanism for adjusting the cross rolls on the frame members 9 closely resembles that described in my copending application, Serial No. 413,051, filed December 10, 1929, and comprises wedge mechanisms 12 for adjusting the angularity of the cross roll shaft 11 in a vertical plane, a screw 13- for adjusting the cross rolls toward or away from the axis A of the material, and coupling mechanism 14 whereby the cross roll shafts are connected to fixed drive shafts 15.

Figure 3 illustrates a pusher 16 in the form of a screw h ld against rotation in any suitable manner, and arranged to be advanced or retracted by means of a nut 17 carried in a frame 18 and having thrust rings 19 formed thereon. In Figure 3 the mandrel, which has been omitted from Figure 1 for the sake of clearness, is indicated at 20. The nut 1'7 carries a set of gears 21 forming part of a change gear set indicated generally at 22. The change gear set, in turn, is driven through a change gear set 23, and this is driven through bevel gears 24 from a shaft 25. The shaft 25 is connected to one of the driving spindles 15 for the cross rolls through bevel gearing 26. It

, will thereby be seen that the rate of feed of the billet, as determined by the pusher, bears a fixed relationship with the speed of the cross rolls, and that any desired ratio between such speeds may be obtained by adjustment of the change gear sets 22 and 23. If desired, a pusher may be actuated by a variable speed motor which is regulated in accordance with the roll speed.

In order to provide for all of the factors encountered in cross rolling, it is highly desirable that the several adjustments be effected sim ltaneously. The machine illustrated in Figure 1 provides for adjusting the angularity of the cross roll shafts in the horizontal plane, and the other adjustments must be independently made for the several rolls. The mechanism illustrated in Figure 4 offers advantages in this respect since a single adjustment serves for all of the rolls.

The mill shown in Figure 4 is provided with a main frame 32 having socket-like housing portions 33 to receive bearing housings indicated generally by the reference character 34. Each earing housing is provided with a spherical portion 35 movable in the housing 33, whereby universal movement of the bearing 34 is secured. Each bearing 34 carries a cross roll 36 on a shaft 37.

It is necessary to drive the cross rolls through suitable gearing, and in order to adjust the mill for different rollings, it is also necessary to shift the axis of the cross rolls and to move them along such axis. For the sake of clearness in description, a tilting of the axis of a cross roll in the plane of the paper will be referred to as a tilting adjustment. A similar adjustment in a plane at right angles to the paper will be termed an oblique adjustment; and an adjustment of the cross roll along its axis will be termed a longitudinal adjustment.

Driving mechanism The main frame 32 is provided with a central opening to accommodate the material being rolled and the mandrel which may be employed. The mandrel is omitted from Figure 1 for clearness in illustration, but is shown in Figure 2. The frame comprises airing-like portion 39 having a bearing brass 40 on the outer portion thereof. A ringgear 41 rotates on this bearing. The ring gear is provided with spur teeth 42 meshing with a pinion 4-3 on a drive shaft 44. The ring 41 is also provided with bevel teeth meshing with bevel gears 45, there being a bevel gear for each cross roll shaft 3'7. Each gear 45 is substantially enclosed in its bearing member 34 as shown in the drawings.

Each bevel gear is mounted on a double universal joint or gimbal comprising rings 46 and 47 having pins 48 and 49 respectively. The pins 48 of the ring 46 engage sockets in the gear 45, whereas the pins 49 are arranged at right angles to the pins 48 and are socketed in the ring 46. The ring 47, in turn, is trunnioned on pins 50 carried by a collar 51 surrounding the cross roll shaft 37. The collar 51 is restrained against longitudinal movement by a holding ring 52 secured to the bearing member 34. However, as shown in the drawings, the shaft 37 is slidable in the collar 51 so as to permit of the longitudinal adjustment.

It will be seen that with this mechanism the cross roll shaft will be driven at uniform velocity regardless of 'what adjusted position the shaft 37 may be in. The bevel gear 45 is held in proper position relative to the ring gear 41 by means of a flange 53 formed on the ring gear and which prevents the bevel gear from getting out of mesh.

Tilting adjustment The cross roll shaft 37 is provided at its rear end with thrust rings meshing with corresponding grooves in a rear bearing 37a. The bearing 37a is provided with a flanged end SllllOllIldGd by a yoke 61'to which a threaded post 82 is rigidly connected. The post extends through slotted openings in a pair of spaced arms 63, the adjacent surfaces of these arms being machined to receive the cylindrical faces of bearings 64. The bearings Oblique adjustment Each pair of arms 63 is shown mounted on a circular disc set into a corresponding recess in the main frame 32, and held in place by a' retaining ring 81. It will be seen that rotation of the disc 80 will be effective for changing the inclination of the post 62 and thereby altering the obliquity of the cross roll shaft. Furthermore, such adjustment leaves the tilting adjustment substantially unaiiected.

The rotation of the several discs 80 is obtained by a ring gear 82 having worm teeth 83 formed on the periphery thereof, these teeth meshing with a worm 84. The ring gear 82 is also provided with bevel gear teeth 85 meshing with corresponding teeth on one of the arms 63 of each disc. Rotation of the worm 84 is therefore eiiective for rotating the several discs 80 and effecting the oblique adjustment of the cross rolls.

Longitudinal adjustment Each rear bearing 37a makes a threaded connection with the bearing member 34, and therefore rotation of the bearing 37a will cause longitudinal movement of the shaft 37. In order to efiect such movement there is provided a worm gear which is connected to the bearing member 37a through a universal joint or gimbal 91. The worm gear 00 meshes with a worm 92 on a shaft 93, this shaft having a universally adjustable bearing 9a in a bracket on the main frame. The shaft 93 is provided with a bevel gear 95, connected to the shaft through a universal joint or gimbal-and meshing with a ring gear 96, which may be rotated in any desired manner.

The shaft 93 is held in the proper position relative to the worm wheel 90 by a casing which has been omitted for the sake of clearness in illustration. Rotation of the ring gear 98 is effective for threading the bearing member 37a in or out of the bearing members 34, and when adjusted, the former are held in adjusted position by lock nuts 97.

By the mechanisms above described every necessary adjustment for the cross rolls can be readily made. The several rolls are simultaneously and equally adjusted, thus effecting marked time savings and insuring that the product will be properly engaged by the rolls .and making certain that the required setting may be accurately and expeditiously eiiected. Y

Pusher mechanism the tube or billet being worked. Each arm .101

carries a pivoted rod 104 extending through an opening in a flange 105 and surrounded bya compression spring 106, the force of which, is adjustable by nuts 107 threaded on the guide pin 104... The action of the spring is limited by a stop 108 formed on the head of the pusher 100;

It will be seen from the foregoing that the rollers normally lie in the position of Figure 5', but that their supporting arms 101.1nay be swung outwardly from the axis AA of the machine. It is particularly to be noted that the tube or billet is engaged by the rollers 103 at points spaced from the axis A-A a distance less than the axes of the pivot pins 102 are spaced. The resistance of the tube or billet to forward motion therefore 1.

tends to rotate the arms inwardly toward the axis, which inward motion is prevented by the stops 108. Therefore no load is imposed on the springs 10-3 by this action.

However, when the rolling has progressed to l the point where the end or" the billet or tube is ready to pass over the mandrel M, as indicated in Figure 5, the edge 109 of each roller engages the Working surface of the mandrel M and there is thus exerted an outward force which swings the arms 101 around their pivots 102; the rollers 103 thus moving over the surface of the mandrel and continuing to exert pressure on the material being worked.

In the form of the invention illustrated in Figure 7, wherein there is shown an arrangement for reducing the diameter of a hollow tube, the pusher 1101's provided with a head 111 on which an arm 112 is pivoted at 113 and provided with a spring mechanism similar to that shown in Figure 5. The arm is provided with an adjustable stop screw 11% hearing against a lug 115 on the pusher head. The arm 112 carries a roller 116 which feeds the tube T forwardly, and when the trailing end of the same has reached the working zone, the edge of the roller 116 engages a fixed guide 117 effective for swinging the arm clockwise as viewed in Figure 7, and causing it to continue to engage the trailing end of the tube through the working zone of the mill.

Roll construction Material economies can be efiected by making the rolls in separate pieces. It is also possible to so construct the rolls that relative rotation between certain of the parts may be had. This latter feature is particularly-desirable where the roll is provided with a smoothing portion which engages the tube after the same has been formed to its final diameter.

The form or roll shown in Figure 4 comprises body portions 36a and 35b and a smoothing cone 36:1. The smoothing cone is held in place by 'a flange 120 and bolts 121. The amount of pressure exerted by the smoothing cone 36d should be relatively light it the cones are attached in the cross rolls proper in such manner as to rotate with th m. However, if desired, the cones may be rotatably mounted on the cross rolls or their shafts and, if necessary, ball or roller bearings may be employed. While the mills shown in Figures 1 to 4 give a Wide range of adjustment,it is still desirable to have the segmental roll so as to permit of changing its contour with the least trouble and expense.

In Figure 8, I have illustrated a modified form of cross roll adaptable for rollingv various sizes of tubes. In this form of the invention the roll shaft cured a cap 132 by a bolt133and washer 134, and

a smoothing cone 135 by a flange 136 and bolts 137 in a bolting ring 138. Figure 9 shows the same roll body in another setting wherein it has been reversed end for end and has been provided with another cap 132a and another cone 135a. This type of construction makes it possible to use a single roll body in obtaining different roll contours.

Referring to Figures 10, 11 and 12, I have illustrated a billet I) having an axis aa and a cross roll R of the conical type. For simplicity of illustration only one roll is shown. A suitable mandrel is indicated at m. The apex a of the cross roll cone lies in the axis aa. If we consider that the work is being done along the outer surface of the metal, it will be seen that the steel as it is formed on the mandrel is in the shape of a frustum of a cone which is in pure rolling relationship relative to the roll R. Therefore there will be no tendency for self-feeding and no tendency to twist the metal either forwardly or backwardly. I Figiu'e 11 shows the roll R tilted so that its apex a lies to the same side of the axis aa as does the body of the roll R. A mandrel m has been substituted for the mandrel, this mandrel being of such size that the medium tube diameter remains the same as in Figure 10. The conditions are now such that the metal at the point where it leaves the grip of the cross rolls will be twisted forwardly and thinned down. Hence there will be produced a thin, long tube, as compared with the setting of Figure 10 which produces a tube of medium thickness and without any elongation of the billet.

Coming now to Figure 12, I have shown the roll R cooperating with a mandrel 1n and so tilted that its apex 0: lies to that side of the axis aa opposite the side on which the roll body R resides. This causes a backward twisting of the metal during rolling, shortening of the billet and the tube wall is thicker than in Figures 10 and 11. The amount of forward or backward twist and the various other factors can be controlled by adjusting the rolls in varying degrees in the fashion indicated.

If desired, the roll may even be swung to such a point that its smaller end engages the material at its point of largest diameter, as indicated by dotted lines in Figure 10, and also as indicated in dot-and-dash lines in Figure 1 as well as in Figure 3, showing the reversibility of the roll constructed as shown in Figures 8 and 9. This gives a very great backward twist and a greatly reduced selffeed, thus bringing about an increase in wall thickness, as indicated in dotted lines in Figure 10, and a shortening of the billet.

In Figure 13, I have indicated a pair of rolls 200 having conical faces which are effective for producing forward twist for a billet which is to be reduced in size and also for increasing the self-feed. These rolls are particularly well adapted for rolling to smaller size because they grip the billet on a larger arc than convex rolls.

'If desired, ring rolls, as indicated in Figures 14 to 16, may be employed. In Figure 14 there is shown a ring roll 201 driven through a gimbal 202 and engaged by a pressure roll 203 which maintains the angularity of the working portion of the roll. A conical roll 204 is employed opposite the ring roll and may be replaced by a pair of conical rolls. This type of roll gives forward twist to a billet which is to be enlarged, thus resulting in a relatively thin wall. In the showing of Figure 15, however, the ring roll 205 is adapted to produce a large wall thickness when enlarging or a thin wall thickness when throttling down. The roll of Figure 16 has a double working cone, such that one cone gives backward twist and the other gives forward twist to the billet. This roll may be used to advantage in special cases, particularly if a large amount of one size of material must be rolled.

I have illustrated and described a present preferred embodiment of the invention and certain modifications thereof. It will be understood, however, that it is not limited to the forms shown but may be otherwise embodied or practiced within the scope of the following claims.

I claim:

1. In a cross rolling machine, a pusher having a pivoted arm for engaging the piece which is to be worked, and yieldable means urging the arm in one direction.

2. In a cross rolling machine, a pusher having a pivoted arm for engaging the material to be worked, and means bearing against said arm for effecting swinging thereof.

3. In a cross rolling machine, a pusher having a material-engaging portion movable radially thereof, and a mandrel, self-acting means for maintaining the material-engaging portion in effective position, and means whereby said portion, when engaged by the mandrel, is moved outwardly thereby.

4. A rolling mill comprising a frame having a central opening, roll shafts journaled in universally adjustable housings on said frame, means for effecting an equal and simultaneous universal adjustment of said housings, and means for effecting a simultaneous and equivalent longitudinal adjustment of said shafts in said housings.

5. A rolling mill comprising a frame having a central opening, roll shafts journaled on axially adjustable bearings in universally adjustable housings on said frame, means for effecting an equal and simultaneous universal adjustment of said housings, and means for effecting a simultaneous and equivalent longitudinal adjustment of said shafts in said housings, including independently operable ring gears and pinions meshing therewith, universally mounted on adjusting screws.

6. In a rolling mill, a plurality of roll shafts spaced from a common axis, and journaled in adjustable bearings, common means for altering the angularity of all said shafts to the axis to the same extent, and common means for effecting equal, simultaneous, longitudinal adjustments of said shafts.

7. Tube making apparatus comprising forming means and a blank pusher having pivoted blank engaging arms adapted to form rigid extensions of said pusher when engaging the blank, and means for yieldably sustaining said arms against displacement by engagement with said forming means.

8. Tube making apparatus comprising forming means and a blank pusher having pivoted blank engaging arms adapted to form rigid extensions of said pusher when engaging the blank, and to yield radially of the blank when engaged by an obstruction such as said forming means, and means for restoring said arms to their rigidly extending position.

9. In a cross rolling mill, the combination with a spherical universally adjustable bearing housing, a roll shaft journaled in said housing, and means for driving said shaft including a gear ring within said housing surrounding the shaft and a'universal joint between the gear and the shaft.- 10. In a cross rolling mill, bearing housings having spherical surfaces, means for supporting said housings for universal movement, roll shafts journaled in said housings, means for adjusting said shafts axially of the housings, means for adjusting said housings in their supports, and common means for driving similar adjusting means for all the housings. Y Y I 11. A cross roll comprising a body-portion, a removable head secured thereto whereby the effective length of the roll may be changed, and a sleeve removably attached to-the-other end of "the roll for engaging the work after deformation by the body portion of the roll.

12. A cross roll comprising a body-portion reversibly mounted on a driving shaft, a head removably-securedto one end of the body portion, and a sleeve removably secured to the other end thereof, said head and sleeve being reversible one for the other.

13. A cross roll comprising a body portion for engaging and deforming the work, a removable head on one end of the body portion, and a removable sleeve on the other for engaging the work before and after deformation by the body portion, said head and sleeve being interchangeable end for end with said body portion.

14. In a rolling mill, a main frame, a plurality of bearing housings mounted therein for universal movement, roll shafts mounted in said housings, means common to all said housings for varying the angularity of said shafts to a common axis, and means common to all said housings for varying the obliquity of the shaft axes to said common axis.

15. In a cross rolling mill, a frame, sockets formed therein symmetrically about a common axis, spherical bearing housings seated in said sockets, cross roll shafts journaled in said housings, means common to all said housings for varying the angularity thereof to said common axis, and means common to all said housings for shifting said shafts axially relative to said common 16. In a cross rolling mill, a main frame having bearing housings supported therein by balland-socket members, cross roll shafts journaled in said housings, means for adjusting the anguqlarity of all said shafts with respect to a common axis, means for adjusting all said shafts axially relative to said axis, and means for adjusting the obliquity of said shafts to said axis, all said adjusting means being common to all .1 said bearing housings.

'21 roll shaft, a bearing housing for supporting the shaft, means for universally adjusting the bearing housing, a drive shaft and a coupling for said roll shaft, and means effective on adjustment of said housing in a horizontal plane for rotating 1? said housing about an axis passing through the junction of the coupling with the roll shaft.

19. In a rolling mill, a roll shaft, an adjustable housing for supporting said shaft, said housing .being rotatable about an axis external thereto to adjust said roll, a drive shaft, a coupling between. thedrive shaft and the roll shaft, and means effective on rotation of said housing about said axis for shifting the housing 'on an axis passing through the junction of the coupling and the roll. shaft.

20. In a rolling mill, a bed plate rotatable about a fixed axis, a bearing housing on said be'd plate rotatable about another axis, and means operated by rotation of the bed plate on its axis for rotating thebearing housing on its axis.

21. In a rolling mill, a bearing housing for a roll shaft, means for adjusting said housing in a vertical plane including a curved supporting foot and a correspondingly shaped shoe therefor, a drive shaft and a coupling for driving the roll shaft, the junction between the coupling and the roll shaft being coincident with the center of curvature of said foot.

22. A pusher for a rolling mill having cross rolls comprising a thrust-exerting member, and means projecting radially from said member adapted to engage the work and pass between said rolls.

23. A blank pusher for tube-making apparatus having forming means, comprising a thrust-exerting member, and Work-engaging means movably mounted thereon for displacement by engagement with said forming means.

24. In a cross rolling mill, a plurality of spherical bearing housings mounted for universal adjustment, spaced bearings in said housings, roll shafts having their opposite ends journaled in said bearings, and a common drive means for the several cross rolls, including gears mounted on said shafts between said bearings for universal movement relative to the shafts.

25. In a cross rolling mill, a frame, a plurality of sockets therein, spherical bearing housings seated in said sockets for universal adjustment relative thereto, a pair of spaced bearings in each housing, a roll shaft journaled in the bearings of each housing, posts operatively connected with the bearing housings, and means for simultaneously adjusting said posts.

26. In a cross rolling machine, a pusher for a billet to be worked, work-engaging members pivoted to said pusher, and means for causing movement of the members in planes radial to the pusher.

27. In a cross rolling machine, a pusher for the work, an arm pivoted to the pusher, means for causing angular movement of the arm in a plane radial to the pusher, and a roller on said pivoted arm for engaging the work.

28. A cross roll comprising a body portion, and a plurality of interchangeable heads therefor, said heads having working cones of different lengths and being attachable to said body portion whereby the small diameter of the roll is adapted to engage blanks of different diameters without changing the adjustment of the roll.

29. In a rolling mill, a roll shaft supported in a bearing housing, means whereby said housing may be adjusted about an axis external thereto, and means for shifting the housing about an axis therethrough, parallel to but spaced from the first-mentioned axis on movement of the housing about the latter.

30. In a rolling mill, a roll shaft supported in a bearing housing, means whereby said housing may be adjusted about an axis external thereto, and means for shifting the housing about an axis therethrough, parallel to but spaced from the first-mentioned axis on movement of the housing about the latter, said last-mentioned means including a toothed segment on the bearing housing and a similar fixed, cooperating member.

31. In a cross rolling mill, a frame, a socket in said frame integral therewith, a bearing housing having spherical portions seated in said socket, said socket having spherical portions engaging said housing, bearings in said housing diametrically opposite each other, a roll shaft having its opposite ends journaled in said bearings, and a removable central ring in said frame engaging a spherical portion of the housing.

32. In a rolling mill, a ring gear, a ring roll disposed within said gear, and a gimbal ring between the gear and roll pivoted to both of them, permitting universal movement of the roll in the gear.

33. In a cross rolling machine, the combination with a main frame having a spherical socket, of a spherical bearing housing seated in said socket, a shaft journaled in said housing, and spaced bearings in said housing engaging opposite ends;

of the shaft, and means for efiecting universal movement of the bearing housing to adjust the,

inclination and obliquity of the roll axis.

34. In a rolling mill, a roll shaft, a drive shaft,

and a coupling spindle therebetween, a shiftable.

bearing housing for supporting the roll shaft, and

means for equalizing the angles between the roll.

shaft, the coupling spindle, and the drive shaft upon an angular adjustment of the roll shaft relative to the drive shaft.

35. In a cross rolling mill, the combination with cross rolls and a pusher for feeding material be-,

tween the rolls, of common driving means for the rolls and pusher, and a speed-change gear between said means and said pusher.

LEO BECKER. 

